Vibrating tool metalworking machine



H. ERNST ET AL VIBRATING TOOL METALWORKING MACHINE March 16, 1937.

Filed Jan. 2, 1935 5 Sheets-Sheet 3 w a m 2 3 43 m of, o W I. v, l v o w.i u .A Vul 1 V7 an 4 n, n, IIIJIII l \/9/ 274 g INVENTOR HANS ERNST BYMAR/o E. MARTELLOTTI MQ/.m4,

n ATTORNEY.

VIBRATING TooL METALWORKING xvmriINE` Filed Jan; 2, `1935 Y v v 49 l v43 m 4a f Ff' *f/l/ zg ,117,32 Illy/11W- J'a-r* INVENTOR.

f zHANS ERNST' BY MAR/.0 E. MARTJEQITOTHI if-a MW' y' ,I

1 ATTORNEY.

Patented Mar. 116, 1937 PATENT ,ol-Fica VIBRATING 'Toon METALWQRKING YMaennmp, i

"Hans Ernst and Mano nMaruotfi; cincinnati, Ohio, assignors to TheCincinnati Milling Ma,... chine Company, Cincinnati, Ohio, a corpora,-

tion of Ohio Application January 2, 193.5.Serial No. 138V `14 claims.(cito-#eti l Ybe carried out wit f "This `invention relates tomachineAtools and 1 more particularly to precision metal cutting m'a-v ichines. l 1 i In the removal of metal with cutting tools, certainwell-known dilculties arise which render `these tools ineiiicierit,` andtheresults accomplished therewith unsatisfactory from the Vpoint `fofiinish obtained. 1`

" The ineiciency ofsuch tools arises `from the iact` thatafter thecutting edge of the tool becornes imbedded inthe metal, it isin`continuous1 i" contact throughout the 'cut with the result thatarpsfeu'do-cutting edge is built upfrom the material being removed; and'although this edge may be of sufficient hardness it nevertheless doesnot form an 4efficient cutting" edge whereby the separation `of the chipmetal from the main body is` more of a tearingoperation than atruecutting operation. Furthermore, these tools have a gorlarg'eincluded cutting angle of anywheres from SOdegrees at a minimum to 80degrees or more,

f and the abrasive action on the tool surface;` in ydeforming the chip,develops a large amount of g heat.` Since the cutting edge of the Vtoolis in constant contact withthe material, it' is im-` possible to applyacoolant to the edge'to pre..

i vent over-heating of the same and it also pre- `vents properlubrication of the surfaces forming f the cutting edge, therebynecessitating more power to eiect metallremoval than would other- `wisebe necessary. t

One of the objects of ythis invention is to prol. vide a machine forremoving metal in'an efcient manner and still produces.` precisionformed and finished surface lin one" passage between the tool and work.Y

Another object of this inventionis to provide a` machine whichwillremove metalwith a mini` mum of pressureion the work, therebysimplifying work holding fixtures and facilitating the machining of4delicate or easily `deformable work i pieces.

i lA further object of this invention is to produce 4r a'metal removingmachine in whichthe cutting Loperation is carried out in such a mannerthat coolant may be eiiic'iently supplied to the cutting edge of thetool whereby the temperature of the entire operation is very low. Y

o An additional object of this invention is to provide afmetal workingmachine'in"` which the i component of force opposing the relativemovement of work and tool is so smallthat in many u cases the work maybe manually moved past the I6 cutter s`o that light machining operationsmay table.

Figure 3 is a view showing one form of vibrat- 20 lire 10.

outthe use of powerV feeding means. f i

`Other objectsand advantages of the'present invention should be readilyapparent by reference kto the following specication considered in con-`junction withthe accompanying drawings illustrav tive of one embodimentthereof, butit will be understood that any modications maybe made yinthe specific structural details thereof within the scope of the appendedclaims without" de@A 10 parting from or `exceeding the spiritrof theinvene tion. v v A Referring tothe drawings/in which like referencenumerals indicate like orlsimilar parts:

`Figure 1 is an elevationof a machine tool emi, 15 bodying theprinciples of this invention. Figure y2 is a section'on the line 2-2 ofFigure 1 showing the antiffrictionally mounted work ing cuttingtool andthe means for eiecting vii hration` -thereof.-

Figure 4 is a section through the housing shown in Figure 3 as viewed onthe line 4--4 thereof. Figure 5 is a section on the line 5 4 of Fig- 25ure 4.

Figure 6 is a section on-the line 8-5-6 of the tool holder shown inFigure 3. y

Figure? is an end elevational view of the tool holder shown in Figure 6.30

' Figure 8 is a. view showing a simplied form of cutter mounting.'v f

Figure 9 is a view illustrating the use of a multiple tooth cutter suchas a broaching tool.'

Figure 10`is a Viewv of a modied form of tool 35 holder. Y y

Figure 11 isa modified form of hydraulic vl'- brator. Y

Figure l2 isa section on the line Ia-Il of Fig" 40 Figure 13 is asection on the line ISI-i3 of Flg-V Figures 14 to 22 inclusive are viewsshowing the relative position' o1 the"'cutting tool and the chip hammerduring one vibratory cycle thereof.

A machine whichembodies the principles oi'V this invention isillustrated in Figure 1 and com-4 prises a column I n having verticalguideways It of the knee for receiving and guiding a second 2 support.such as the saddle Il. A sub-table I8 is suitably guided in the saddlefor horizontal movement which may be effected manually through rotationof a handle I1 operatively con- 8 nected to the end of a screw I9 whichis threaded in a fixed nut, not shown, but carried by the saddle Il.

The screw may be rotated from a prime mover I9 carried by the column andinter-connected 10 through suitable transmission means to the gear 20 asshown in Figure 2, which is iixed to the end of rotatable shaft 2|.'I'his shaft carries at its up-A per end a bevel gear 22 whichinter-meshes with l pair of bevel gears 28 mounted for free rotation 15co-axially of the lead'screw I8. These gears are adapted to beinter-connected with the lead screw through the shiftable clutch member24 having a shifter fork 28 xed on the slidable shifter rod 28. This rodmay be shifted through suitable in- 20 ter-connecting means 21 to themanually rotatable handleY 28 carried by the saddle.

The sub-table I6 has guide surfaces 28 and 80 formed thereon forinter-engagement with complementary guide surfaces 3l and 32 formed on25 the under-side of the work support 88.V To insure a proper nt, a gib84 may b e interposed between one pair of these complementary surfaces.y

The ,weight of the table 88 is transmitted to the sub-support I8through. the agency ,of anti-fric- 30 tion members 95 which facilitateeasy movement ofthe table 88 and make it possible for the same tobedirectly pushed manually; and to facilitate this a handle 86 is securedto one end of the table, as more Yparticularly shown in Figure 1. Suit-35 ablemea'ns, such as flanges 31, may be tted on the sub-'support forengaging surfaces 38 of the table to prevent lifting of the same.

`When it is desired to move the work table 88 by the power meansdescribed heretofore, the 40 same may be locked to the sub-support bythe locking screws 39. A The table 83 hasT-slots 48 formed in the topsurface thereof in which may be mounted T-bolts 4| for securing workholding xtures, such as the angle blocks 42, between which a work piece48 maybe secured.

Assumingthat a precision finished surface is to be formed on the work inthe plane of the dotted line 44 shown in Figure l, a tool having a cut\0 ting edge 45 and carried by a bracket 48 is fixed with the column I9of the machine as by a dovetailed guideway 41 and the knee verticallyadjusted so that this cutting edge lies in the plane of lthe surface tobe formed.

An analysis of cutting action by conventional tools shows that theprocess of removing material is in reality a combination of twoindependent functions; viz, first the severing or separation of y thechip from the body of the work piece, and second the deformation ordistortion of the chip necessary to move it out of the path of theadvancing tool. The combination of Vthese two functions in a single toolis a compromise and as such does not permit thetool to either cut orbend the material in the most eiilcient manner. By the use of a compoundtool in which the two functions arel performed independently, eachfunction may be 'performed in the most eilicient manner. To this end thetool is provided with two members.l onela cutter 48 which performs thefunction of severing the chip by actual cutting, and the other a chiphammer 49 which performs the function of deforming or bending the chipYafter it has been separated by the tool 48.

As previously mentioned, conventional preci- Vwithdrawing the tool fromthe work so that the coolant may penetrate to the actual point ofcutting. In other words, the cutting tool 48 is oscillated or vibratedduring' the cutting action in a definite plane relative to the work, andthe frequency of this vibration is very high, ranging from`approximately a hundred Vto upwards of a thou- Y sand cycles per secondor more as the case may require. VThis is to be distinguished from theconventional, manually guided, non-precision, low frequency, singlepoint vibrating tools, such as air hammers and the like. In order toprevent interference between the two functions of chip sever-4 ance andchip deformation, the one should preferably be carried out in adiii'erent phase relation to the other. In order to understand morefully the manner in which this is accomplished, reference may now' behad to Figure 14 to 22 inclusive which represent the various positionsof the cutting tool and hammer through one cycle of movement. l

In Figure 14 the work piece48 is assumed to be feeding at a constantrate in the direction of the arrow 50 and at the instantaneous positionof the parts the cutter 48 is stopped and the hammer 49 is stillretracting in the direction of the arrow 5|. understanding the relativeposition of the parts throughout the remaining figures, a fixedreference line 52 has been drawn and this may be.

assumed to be 'drawn on a fixed part of the machine. From the remainingviews it will now be seen that the work piece 43 is continuouslytraveling toward this line, ywhile the cutter andY arrowv 88 toward thework and during this same time interval the workpiece 49 has advancedtoward the line 52. At the same time the hammer 49 has been retractin'gand has just reached a stop position at the instantaneous position ofthe parts in this figure. Although the hammer appears to have advancedin comparison with its position shown in Figure 14, this is merelyrelative due to the fact that the hammer is carried by the support whichcarries the cutter 48 so that although it has been retracting itselfrelative to the cutter 48 still at has been bodily moved through spaceby the cutter support, and the resultant of these two movements is thatthe hammer is really further from the line 52 than it was in Figure 14.

In Figure 16 the work has advanced another increment of movement towardthe reference line 82 and at the same time the cutter has departed fromthat reference line a sufficient amount to For the purpose of morereadily In the' make a small incision in the work. In this iig- 4 hammerhas followed up fthe movement of the cutter and deformed this chipportion to a `much `greater extent `than-would have been the case hadthecutter 48 been Vacting alone.

In Figure i8 the cutter has reached a4 position lof maximum "departurefrom the reference line 52 and is instantaneously stopped while thehammer hasbeeniollowing up the movement ofutlzue`` cutter andfurtherdeformingthe chip.` r In Figur`e`19` the cutter has started itsreturn stroke while the hammer has continued its adiY vance `and hasjust reached its stop position.`

. InV `Figure 20the hammer and cutter are re# tractingand itwillbe notedthey are both retractingatad'aster rate than the advancing movement `oi?the work.` This allows va coolant' r of `lubricantto enter `the cut orincision and properly lubrlcatewthe parts for the next cutting stroke.In Figure 21 thecutter andhammer are still returning and in Figure 22the cutter hasy reached astop positionv which `'corresponds to its stopposition shownin Figure 14, thus completing one cycle of movement. yItwill be noted in -ing or ripping action.

these figures that the cutter has a very small includedanglesothat itsaction on the work` main `in contact @with-` the `finished face 44throughout u the* remainder of the' cut, `and -thecontinuousreciprocation ofthe face upon the faceofgthe work tends to burnish this,surface whereby the result is a precision surfacefas wellasahighlyilnished surface.` However,` even `if a smallclearance anglewere provided, a highly iinlshed surface wouldstill be produced onv thework; due `toH the.. absence of anyfppreciable pseudocuttihg edge with`this method of cutting. The-length" of` stroke oithecutter and the,

amount of. work advanced during a single stroke has`been'greatlyexaggerated in Figures 14 to 22 in order" to vexplain" therelativeposition `of thel parts during one cycle .ot operation.` As" amat ter of `fact, the cutter andhammer are vibratedlV `at relativelyhigh `frequencies as previously sug- 55 f tool and hammer is shown inFigure 3 in which gested,l and therefore the length of their Vstroke isvery smalLf none marinero; vsupporting and vibrating the *theslupportlull` is shown as provided 'with a cylin-Y dricalborer' in whichis reciprocably or oscillatably `mounted a plunger 5l having a central tor axial bore `5B. Qneend of' the. bore 5B `is closed or sealed bytheplate 59 which is held in place by a pluralityy of lister head screws60; A plugfGZ is threaded inthe end of boref` of.

vthe plunger 51 forclosing the end` thereof. 1 v The plunger 5l has .anenlarged head G3 in the lower side' oi-` which is formed a rectangular-NgrooveSlin which is xed the c utterdil, `the 1 "13 "ffiw samebeingheld therelnby set.. screws 65. One? end of thegroove is closed by theportion 66 as shown in Figure `3 through whichis threaded a` A set screwBTforidete'rmining the axial position of the cutter. r

The member 63has a rectangular-shaped vguide portionwhichiitsinto asimilar shaped openaorsav ing in a rted guide block 69 which is securedto the member 46 as by the screws ll. Suitable adjustable `gibs Il maybeinserted between the guide portion 6% and the block 89 and these maybe held in position by the flat headed screws 'l2 having locking nuts I3on the end thereof. This construction prevents rotation of the plunger51 and insures that the surface 55 of the cutter lie parallel to thesurface being formed.

Thehead'l has a pair of holes 15 drilled in one end"`face thereof `andon opposite sides oi thecenter`for..receiving springs 'l5 which abutagainst nanges 1s vcarried by the block sa and which overlap.thes'ellioles when the block'is `secured in position.`^The A springsreactagainst these vflanges, tending `to v urge the plunger 51 towardtheright as viewed in Figure 3. Reciprocation of the plunger 5l is eiectedby admitting uid pressure through the 'port Il which acts on the rightend of the plunger, moving the same toward the left and compressing thespring;

When this pressuredrops below` the resultant force of the springstheplunger is shifted toward the" right. Thus by raising and lowering thepressure atport 51 above and below the capacity of the springs theplunger 51 andthereby the tool 48 will be vibrated and at a ratedepending upon the rate at which the hydraulic pressure is varied.

"The hammer 49 is'secured inthe end of a second plunger 18 which isreciprocably mounted in an inclined bore`19 `which bore intersects thehorizontal bore 58 formed axially ofthe plunger 5l.` The hammer is soshaped and held by the plunger that its lower face BIJ rides on thel`upper face of the cutter. r r r An-abutment member 8| is` secured tothehead 68 for engaging one end ofa spring 82 which is vmounted in abore 83 formed in the plunger 18 and which acts on the plunger to" shiftthe same in adirection to cause retractionoi the hammer. Since the bore58 is closed bythe plug62 it acts as acylinder, whiletheplunger 18 willbe moved `upon Vadmission of pressure thereto. A port B4 isformed in thesupport 46 and is always in communication` with anannular groove YB5formed onwthe periphery of.` the plunger 51 andl this annular groovehas. a pair of opposed radially extending openings it formed `thereinthrough l which uid pressure 'is conducted `to the bore -orcylinder 5tregardless of its longitudinal position.` It will now be seen that `by`having indie--l y pendentsources of pressure at ports il and 84 theplunger 51 may be vibrated at any desired frequency and that thieVplunger i9 may be' .vibrated at the same or dierent frequency and in thesame or different phase relation relative thereto, whereby the variousmovements described in connection with Figures 14` to 22 may be?obtained. in order to insure that `all air. is removed from thesevarious spaces so that true results may be obtained, a pair of bleederchannels 'i and t8 are formed in the block 46 and.

communicating respectively with the annular groove 85 and the space atthe right end of bore 5 to permita constant leakage` of oil from thesespaces and `thereby carry' off any air that may accumulate therein. tThese bleeder channels ter` minate in bleeder coils 89 andV 90respectlvelyn which, canl be made of suitable resistance depending `uponthe amount of bleed found desirable and necessary to eliminate theairfrom the system and may be made different for each channel. As amatter of convenience, the bleeder coils lmay be finally connected to a'common return channel 9i wherebyl the "escaping oil may be returned toa common reservoir 92. Since air may also collect in the bore 59, anadditional bleeder channel 93 may be provided at the point ofintersection between bores 58 and 19 and this channel may also terminatein a bleeder coil 94 of suitable resistance.

Vibration of the fluid pressures acting on the tool and hammer may beeffected in various ways and one form of accomplishing this is shown inFigure 3. A pair of channels 95 and 96 connect the ports 04 and 11respectively to ports 91 and 08 oi what may be termed the pressure wavegenerator 99. The ports 91 and 98 are in the :form of cylinders in whichare reciprocably mounted the pistons and |0| respectively. Thesecylinders are supplied with fluid from a constant delivery pump |02which has an intake |03 through which iluid is withdrawn from thereservoir 92 and delivered under pressure into the channel |04. The`channel |04 has a bypass relief valve |05 connected thereto throughwhich excess fluid may be returned to reservoir. This channel also hasconnected thereto a pair of check valves |00 and |01 through which uidis delivered to cylinders 91 and 98 respectively when the pressuretherein drops below the pressure in channel |04. The pump |02 thereforeserves to maintain the entire system filled with oilk under apredetermined pressure determined by th'.l setting of the relief valve|05.

Ii the channel 96 and the parts supplied thereby are filled with oil andthen the piston I 0| be suddenly moved toward the left as viewed in Fig.3, It will be apparent that a wave of higher pressure than thatdetermined by pump |02 will be propagated through the line 96, and ifthe value oi this pressure wave is higher than the reaction provided bythe springs 15 an oscillation of the cutter 08 will be effected.Similarly a movement of the piston |00 toward the left will propagate -apressure wave through the line 95 and cause an oscillation of the hammer49. Means have therefore been provided for oscillating the plungers |00and |0| at a relatively high frequency in order to produce a rapidsuccession of pressure waves and thereby a vibration of the desiredparts; l

The mechanism for oscillating the plunger |00 is shown in Figure 4 andcomprises a cam |08 which is secured for rotation to the shaft |09 whichin turn is driven by suitable power means such as a motor I|0 as shownin Figure 3. The cam |08 has a cam groove I I| which is so shaped as tocause a desired number of reciprocations of plunger |00 for eachrevolution of the cam. In the present construction, it is so shaped asto produce four reciprocations for each revolution.

The plunger |00 is pivotally connected by th'e pin ||2 and sliding block||3 to the swinging arm II4 which has secured to its lower end a pair ofrollers II5. One of these rollers engages the outer periphery of the camgroove and the other roller engages the inner periphery of the camgroove and by means of this construction all lost motion may be taken upbetween the cam groove and rollers, and furthermore adjustment may bemade for wear. In order to provide for this adjustment the arm ||4 has aslot IIS cut in the end thereof between the two rollers so that each issupported by a separate portion. An adjusting screw ||1 is threadedin aportion such as ||8 with its end engaging the other portion ||9 so thatupon rotation of the screw in one direction the portions may beseparated and thereby. the rollers moved further apart. The amount ofthis adjustment may be controlled by a pair of screws |20 which are alsothreaded in the portion |I8 but having sliding t in the portion I 9.

The same construction is utilized for reciprocating the plunger |0| aswill be seen from Figure 5 with vthe exception that the cam |2| ismounted on the shaft IIO in out-of-phase relation with cam |08, theamount of this out-ofphase being represented by the acute angle |22.'I'his changes the position of the cam groove |23 which is representedby dotted lines in Figure 4 relative to the cam groove III so that themovements of plungers |00 and |02 may be independent of one another andin such relation as to produce the cycle shown in Figures 14 to 22inelusive.

In order to provide for the contingency that more energy might be putinto the system by the pressure wave generating pistons than is absorbedby the receiving pistons whereby reected waves might be formed whichwill cause an accumulation of energy and thereby anv 1ncrease in 'themaximum pressure to a point that will cause bursting of the pipes, meanshave been provided in the form of closed vessels |24 and |25 connectedrespectively to channels 95 and 96 and of much greater volume than thedisplacement of the pistons to absorb this excess energy and permit thesame to gradually leak away through resistance coils |26 and |21respectively to reservoir.

Another embodiment of the invention is shown in Figures l0 to 13inclusive, in Figures 10 and 12 of which is shown a different form ofsupporting the cutter and hammer for vibration, and in Figures l1 and 13is shown a different form of pressure wave generator.

Referring to Figure 10, the cutter 48 is supported in a head |28 in asimilar manner as before, but the head is attached as by screws |29 tothe end of a pair of plungers |30 and |3| which .thereby does away withthe necessity of providing vguiding means to prevent oscillatorymovement of the tool out of the plane oi the surface to be formedwhichwas necessary in the previous construction where only one piston wasutilized. Each of the plungers |30 and |3I is provided with a spring |32interposed between the closed end 33 of bore |34 and an enlarged disk|35 secured to the end of the plungers. The spring tends to retract thetool and the admittance of hydraulic pressure through port |36 tends toadvance the tool. The disk' |35 has a plurality of smallaxially-extending grooves |31 provided in its periphery to permit a'slight leakage past the same which will find its way to an opening |38in the sleeve |39 and thereby through the space |40 existing between thereduced shank |4| of the plungers and the member |33 to the bore |42which is connected by inter-drilling to the exhaust port I 43. 'Ihisinsures that air will not become entrapped in the system and provides ameans for conducting any air, that may accumulate therein, out of thesystem.

This construction also acts as a relief valve in the sense that whenthere is no load on the cutter, and the pressure has only the resistanceof the spring to overcome, the plunger |30 will gradually be moved tothe left and as it does, the shoulder |4I withdraws from shoulder |42and opens up a gap permitting a freer escape of oil to bore. |42.However, when a load comes on the 35 tlcularly shown in Figure 13.

creased, thereby increasingthe resistanceto flow .and raising thepressure `on the` end of the plunger. Thus the resulting action is todecrease the pressure on the plunger when there is no 5 load, andimmediately increase it when there is a load. i

The hammer 49 is connected to the end of a single plunger |44, it notbeing necessary to provide two plungers to prevent inadvertentoscillation of the hammer because the straight `edge thereof will beprevented from` rotation on each forward stroke bythe plane uppersurface 6|] of thecutter 46. The plunger |44 is fitted ina similarmanner as plungers |30 and |3| with a 16 spring |62 and a disk |35secured tothe end thereof for receiving pressure from the spring.

"e" and is'connected through a pipe |49 to port |56 '30 of thepressureiwave generator 15|. This port communicates with a bore |51.lformed in a sleeve |54 which has cut-away portions |54 on opposite sidesthereof to form'a port through which the huid is delivered to the space|55 as more par- This space is connected by a pipe |56 to the port |36of the cutter plunger cylinders. The sleeve |53 is supported in anadjustable member |51 which has Y a plate |56 secured thereto as byscrews |59. ,The M plate is sufficiently large to cover `the opening |64in the frame |6| into which the member |51 is inserted.` The plate has apair of elongated holes |62 on each side thereof through which 'pass theclamping bolts |64. The member |51 has a pair of sleeves |64 which arein axial alignment and each of which has an opening |65 whichcommunicates to theV space |55 and a port its in the end thereof whichnes adjacent the wheel |61. The sleeve |64 is `secured as by a pin |66to a bolt |69 which passes through an 50 elongated sleeve 3110 which isthreaded into the member |51. The end of sleeve |10 engages the end of-sleeve |64 so thatupon rotation of sleeve v |16 the sleeve |64 andthereby its port |66 mayv `be adjusted toward and from thewheel |61 and55 determine the space or opening between the end of the sleeve and theside of the wheel. The bolt |69 has a threaded end |1| upon which ismounted a nut |12 for holding the sleeve |64 againstthe end of the`sleeve |16.

m In addition to providing individual adjustment of the sleeves |64relative to the wheel |61,

means have been provided for adjusting the member |51 laterally so thatthe sleeve |53 will be lined up with a. bore |13 in which it is slid ("5able.` This means comprises a pairof pins |14 which engage lugs`projecting from member |51 and pick-up screws |16 for lockingthe partsin position. The frame |51 `is vertically adjustable relative to thesleeve |53to position the T0 port |66 vertically while the individualadjustment takes care of adjustment horizontally. By loosening thelocking screws |63 the member |61 may be moved up and down and toprevent leakage from the interior of the generator the 14' member |51 isprovided with trunnions |11 which extend through bushings |18 having aninner flange |19 andan outer washer |60` which is acted upon by theannular nut |61 for securing the trunnion in place after verticaladjustment. The wheel |61 has a plurality of sector-shaped notches`|82cut in the periphery thereof whereby. the fluid escaping from port |66will flow infstrearn Aline form to exhaust and prevent undesirablereactionson the wheel. .From this it will be seen that the pump |46 willll the entire system full of oil under` a predetermined pressuredepending upon the rate of escape through the ports |66. When a space onthe wheel |61, such as |83, is opposite the ports |66, the rate of`escape through ports |66. is materially reduced so that the pressure atthis point will rise and a pressure wave be propagated through the pipe|56. A

A similar system is provided for causing vibration of the` hammer andcomprises a pump |64 having an intake |85 and a delivery channel |86connected to port |81 of the generator 15|. A`

similar construction as that shown in Figure i3 is utilized forpropagating a pressure wave in the line |45 leading to the hammer. Ifitis desired that the hammer oscillate out of phase with the cutter, `thenthe adjustable member |51 is raised or lowered depending upon therelationship desired between the phase of operationof the hammer andthat of the cutter. Although the details of` construction are differentit will be seen that the 'same general principle is utilized in that acolumn of :duid acts on a" plunger and that pressure waves are createdin the column of ud to cause vibration of. the part.

In taking light cuts it .may not be necessary to utilize the .hammerwhereby`only a cutter such as |88 shown in Figure 8` may be utilized,and this may be secured in a head |69 as by a set screw |90 the headbeing integral or otherwise connected to raQpiston |9| and held againsty rotation by a suitable `guide |62. Either `form' of There has `thusbeen provided an improved form of metal working machine in whichprecision Vformed surfaces of high finish may be produced in an efcientmanner with an eco- `nornical yexpenditure of `power and in a singlepass between the tool and the work, eliminatingthe necessity of asubsequent operation to smooth or `Iinish thedesired surface.

What is claimed is; i

1. A machine tool having a work support, a tool support, a cuttermounted in said tool support for feeding movement relative to the worksupport, said cutter having a small acute angular cutting edge formaking incisions in the work-fa hammer-mounted in adjacent relation tosaid edge for entering the incision and deforming the metal, and meansto vibrate the hammer and the tool indifferent. phase relation duringfeeding movement of the work support, including separate hydraulicchannels leading to the hammer and tool respectively and a generator foralternately creating pressure waves in said channels.

2. In a machine tool having a work support and a cutting tool having asmall acute-angled cutting edge, the combination of means for advancingthe work support past the tool at a constant feeding rate, means toreciprocate the cutting edge at a faster rate than said feeding ratewhereby the cutting edge will alternately penetrate the work andwithdraw therefrom, and means to supply a coolant to the tool whereby 10during withdrawal of the tool from the work the coolant will enter theincision so that the metal removing operation may be carried out atrelatively low temperatures.

3. A vibratory cutter for machine tools comprising a housing, a movablemember mounted in the housing and carrying a metal cutting tool,resilient means for moving the member in one direction, hydraulic meansfor urging the member in an opposite direction, and means for rapidlychanging the pressure of said hydraulic means to eect vibration of thetool. 4. A metal cutting tool comprising a housing .having means forattachment to a machine tool in prescribed relation to a work support, amember movably mounted in the housing for supporting a cutting tool,means to effect sudden impacts between the tool and Work, a hammermovably mounted in said housing for entering the incisions alternatelywith respect to the tool to deform the metal to be removed, and means tocause the hammer and tool to vibrate in predetermined out-of-phaserelation with one another, including fluid operable vibrators individualto the hammer and tool, and means to deliver pressure alternately tosaid vibrators whereby they will be actuated in out-emphase relation.

5. A vibratory tool for producing precision surfaces in machine toolscomprising a housing, a piston member` slidable in said housing andcarrying 'a metal cutting tool, resilient means acting axially on saidpiston member, means to produce an opposing hydraulic pressure on saidpiston, and means for eiIecting sudden changes in said pressure aboveand below the pressure of said resilient means to effect vibration ofsaid tool.

6. A vibratory cutter having a housing adapted to be attached to amachine tool, a piston slidably mounted in said housing carrying a cut-60 ting tool, resilient means acting axially of saidpiston to move thetool in one direction, a source of hydraulic pressure connected to act,constantly on the end of said piston in opposition to said resilientmeans, and means to effect sudden in- 55 creases in said pressure tocause vibration of the tool.

'7, A vibratory cutter having a housing adapted to be attached to amachine tool, a piston slidably mounted in said housing carrying acutting tool, resilient means acting axially of said piston to move thetool in one direction, a source of hydraulic pressure connected to actconstantly on the end of said piston in opposition to said resilientmeans, the resultant of said hydraulic pressure being greater than thepressure of said resilient means, and means to cause sudden drops in thehydraulic pressure to cause vibration of said tool.

8. A vibratory cutter having a housing adapted 70 to be attached to amachine tool, a piston slidably mounted in said housing carrying acutting tool, resilient means acting axially of said piston to move thetool in one direction, a source of hydraulic pressure connected to actconstantly on the end of said piston in opposition to said resilientmeans, the resultant of said hydraulic pressure being greater than thepressure of said resilient means, means to cause sudden drops in saidpressure to cause vibration of said tool, said means including a rotarydisk, and means on said disk for periodically connecting said pressureto exhaust.

9. A metal working tool having a housing, a reciprocable plunger mountedin the housing, a cutting tool carried by said plunger, said tool havinga small acute-angled cutting edge, the face forming one side of saidangle being adapted to lie in the plane of the surface to be formed inthe work by said cutting edge, and power operable means effective onsaid plunger to eect vibration oi the tool whereby the edge will severthe metal to be moved and the face will burnish the formed surface ofthe work.

10. A vibratory tool for precision machine tools including a fluidreciprocable member, a cutting tool carried by said member, means tomaintain a column of fluid in pressure contact with said member, meansto vibrate said column of fluid, and a high resistance uid leak forremoving air from said column of fluid.

1l. In a machine tool, the combination of a work support, a toolsupport, a cutter mounted on the tool suupport and bodily movable rela-I,

tive thereto, fluid pressure means for absorbing the entire reaction ofthe cutter under out, and means to vary said pressure to cause vibrationof the cutter during relative movement between the work support and toolsupport.

12. In a machine tool, the combination of a work support, a toolsupport, a tool supported for free bodily movement in a directionparallel to the direction of feeding movement of the work support, fluidpressure means for restraining free movement of the tool, and means tovary said pressure means to cause vibration oi' the tool during feedingmovement of the work support.

13. In a precision machine tool. the combination of a work supportguided for precision rectilinear movement, a tool support, a tool havinga shank also guidedfor precision rectilinear movement parallel to thefirst-named movement, opposed pressure means acting to cause oppositemovement of the tool shank, and means to alternately differentiate saidopposing pressures to cause vibration of the tool during movement of thework support to produce a precision surface on the work.

14. In a machine tool, the combination of means for forming a precisionsurface on a work piece by removing the metal in ribands comprising ametal working tool having a cutting edge substantially equal to thewidth of the riband, means to support the tool for movement in adirection parallel to the surface to be formed whereby the cutting vedgewill be in continuous contact with the work, fluid operable means forreciprocating the tool during relative movement between the work supportand the tool support to eifect alternate cutting and burnishingoperations, and means to eiect a lateral shifting movement between thetool and work to reposition the parts for subsequent removal of anotherriband.

HANS ERNST. MARIO E. MAR'rELLoTrI.

